JP2011185673A - Bearing for timepiece, movement, and portable timepiece - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing for a timepiece, movement and portable timepiece, capable of improving the accuracy of clocking. <P>SOLUTION: The bearing 180 for the timepiece includes a shaft 143 which rotates around the axis, and a bearer 181 which is provided at least at one axial end of the shaft and supports the shaft rotatably. The shaft has a shaft body 140a and a tenon part 145 which is formed at the axial end of the shaft body, and the bearer has a mortise stone 171 wherein a through-hole 172 through which the tenon part is inserted is formed, a jewel 173 which is disposed opposite to the axial end face 148a of the tenon part, an engaging spring 182 which regulates axial movement of the jewel, and a mortise stone frame 174 which encloses the mortise stone, the jewel and the engaging spring. The bearer is held so that it is movable in a prescribed amount axially and radially in relation to a frame, and at least either one of the mortise stone frame and the frame is formed of a magnetic material, while permanent magnets 176 are provided at positions in the other of the frame bodies, opposite to the side of the above one of them, and along the circumferential direction of the shaft. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a timepiece bearing, a movement, and a portable timepiece.

  Conventionally, rotating mechanical parts such as gears used in portable watches such as watches and pocket watches are provided with bearings so as to include the ends of the rotating shafts, and the rotating shafts are guided by the bearings and rotated. By transmitting the torque, the time is recorded. As such a watch bearing, an earthquake-resistant bearing shown in FIG. 14 or a combination bearing shown in FIG. 15 is used (for example, see Non-Patent Document 1).

  Here, the balance of the timepiece is provided with a seismic bearing to prevent breakage of the tenon formed at both ends of the balance which becomes the rotation shaft of the balance when an impact is applied to the timepiece. 16 and 17 show the configuration of a conventional general watch bearing (seismic bearing) 580. As shown in FIGS. 16 and 17, a tapered tenon 545 is formed at the axial end of the rotation shaft (spring) 543, and a bearing 580 is disposed so as to enclose the tenon 545. The bearing 580 includes a frame body 566 supported and fixed to the main plate 567, a cobblestone frame body 574 that is included in the frame body 566 and arranged to be movable in the thrust direction and the radial direction with respect to the frame body 566, and a cobblestone A hole 571 that is supported and fixed to the inner peripheral surface 574a of the frame 574 and has a through hole 572 through which the tenon 545 is inserted, and an axially outer end portion (tenon end surface 548a) of the tenon 545 are configured to be supported. And a presser spring 582 for restricting the movement of the receiving stone 573 outward in the axial direction. The presser spring 582 is supported and fixed to the frame body 566.

  When an axial impact is applied to the rotary shaft 543 of the bearing 580 configured in this way, the hozo 545 pushes the receiving stone 573 and is buffered by the elastic deformation of the presser spring 582, and further the large diameter of the rotary shaft 543. The movement is stopped when the end surface 549 comes into contact with the bottom surface 566d of the frame body 566, thereby preventing the hozo 545 from being damaged.

  On the other hand, when an impact is applied in a direction (radial direction) perpendicular to the axial direction with respect to the rotation shaft 543, the hozo 545 pushes the hole stone frame body 574 and the stone 573 via the hole stone 571, and the hole stone frame body. After the 574 and the receiving stone 573 slide up the slope 566c of the frame body 566, the movement stops when the small diameter portion 546 of the rotating shaft 543 comes into contact with the through hole 566e of the frame body 566. It is preventing. Further, when the impact disappears, the hole frame 574 and the stone 573 are configured to slide down the slope 566c of the frame 566 and return to the original position by the elastic force of the presser spring 582.

“The Theory of Horology” by Swiss Federation of Technical Colleges, 2005, p. 290-291

  Incidentally, in the conventional watch bearing 580 described above, FIG. 18 shows the relationship between the external force and the displacement when the bearing 580 is operated by an impact or the like. As shown in FIG. 18, in the initial state (the state where no impact is applied to the bearing), a pressurization pressure P0 is applied by the presser spring 582, and when the external force exceeds P0, the cobblestone frame body 574 and the receiving stone 573 move. Begins. When the external force further increases, the movement amounts of the hole stone frame body 574 and the stone 573 increase, and the movement stops when the large diameter end surface 549 of the rotating shaft 543 comes into contact with the frame body 566. Here, if the external force immediately before the large-diameter portion end surface 549 comes into contact is P1, P1 needs to be set smaller than the force P2 that breaks the hoses 545. Further, if P0 is too small, the positions of the hole stone frame body 574 and the receiving stone 573 are moved only by applying a small external force, so P0 is desired to be as large as possible. That is, it is advantageous that the slope (spring constant) of the line segment connecting P0 and P1 is smaller.

However, in a wristwatch or the like, the space that can be divided into the bearing 580 is limited, and the outer diameter of the earthquake-resistant bearing is actually about 2 mm. Therefore, it is difficult to ensure a sufficient spring length of the presser spring 582, and as a result, the spring constant is increased to some extent. As a result, since the upper limit of P1 needs to be smaller than P2, P0 must be set smaller.
That is, in the conventional watch bearing 580, the hole frame 574 and the receiving stone 573 are moved only by applying a small external force, the vibration of the bearing 580 (temp) becomes unstable, and the timing accuracy is lowered. There is a problem.

  Therefore, the present invention has been made in view of the above-described circumstances, and provides a timepiece bearing, a movement, and a portable timepiece that can improve timekeeping accuracy.

In order to solve the above problems, the present invention provides the following means.
A timepiece bearing according to the present invention includes a shaft body that rotates about a shaft center, and a bearing body that is provided at at least one axial end of the shaft body and rotatably supports the shaft body. The shaft body includes a shaft main body portion and a tenon portion formed at an axial end portion of the shaft main body portion, and the bearing body is a through-hole through which the tenon portion is inserted. A hole stone in which a hole is formed, a stone positioned opposite to the axial end surface of the ridge part, a locking spring that restricts the movement of the stone in the axial direction, the hole stone, the stone, and A hole stone frame that contains the locking spring, and the bearing body is accommodated so as to be movable in a predetermined amount in an axial direction and a radial direction with respect to the frame body, and the hole stone frame and the At least one of the frame bodies is formed of a magnetic body, and is a position facing the one side on the other side of the shaft body. Is characterized in that permanent magnets are provided along the direction.

  With this configuration, since the magnetic attractive force of the permanent magnet acts in a state where no impact is applied to the watch bearing, the pressurization (P0 described above) can be set large. Therefore, it is possible to prevent the bearing body from moving with a slight external force applied. In addition, by accommodating the movement amount of the bearing body so as to be movable by a predetermined amount with respect to the frame body, the movement amount of the bearing body can be regulated before an external force that damages the relief portion is applied. Therefore, the timing accuracy can be improved.

  Moreover, the timepiece bearing according to the present invention is characterized in that both the perforated frame and the frame are formed of a magnetic material.

  By comprising in this way, the leakage magnetic flux to the exterior can be reduced and the magnetic influence on the components which consist of a hole stone frame and the magnetic body arrange | positioned in the vicinity of a frame can be reduced. Therefore, it is possible to prevent the timekeeping accuracy from being lowered.

  In the timepiece bearing according to the present invention, the shaft main body portion has a diameter larger than that of the tenon portion, and the hole diameter of the through hole through which the tenon portion formed in the frame body can be inserted is It is formed smaller than the outer shape of the portion, and the amount of movement of the bearing body in the axial direction is restricted by the shaft main body portion coming into contact with the frame body.

  With this configuration, since the movement of the bearing body in the axial direction can be reliably controlled, it is ensured that the relief portion is damaged by the removal of the relief portion (shaft body) from the bearing body. Can be prevented.

  In addition, the timepiece bearing according to the present invention has a locking projection formed on one of the frame body and the hole stone frame body, and a locking recess that locks the locking projection on the other side. The axial movement amount of the bearing body is regulated with respect to the frame body.

  With this configuration, since the movement of the bearing body in the axial direction can be reliably controlled, it is ensured that the relief portion is damaged by the removal of the relief portion (shaft body) from the bearing body. Can be prevented.

  Further, the timepiece bearing according to the present invention is provided with an elastic member that elastically holds the movement of the bearing body in the axial direction, and the amount of movement of the bearing body in the axial direction is restricted with respect to the frame body. It is characterized by that.

With this configuration, since the movement of the bearing body in the axial direction can be reliably controlled, it is ensured that the relief portion is damaged by the removal of the relief portion (shaft body) from the bearing body. Can be prevented.
Further, the magnetic attraction force of the permanent magnet decreases as the bearing body moves away from the frame body, and the reaction force of the elastic member increases as the bearing body moves away from the frame body. Therefore, by combining the different characteristics of the magnetic attractive force of the permanent magnet and the elastic force of the elastic member, the change in the force applied to the bearing body can be reduced. Therefore, since the pressure can be set to be sufficiently large and smaller than the force that breaks the ridge part, the bearing body can be made difficult to move with respect to the frame body even when an external force is applied, and the impact etc. Thus, even if the bearing body moves relative to the frame body, it can be reliably returned to the original position.

  A movement according to the present invention is a movement of a timepiece including a barrel, a watch wheel, a escape wheel, an ankle, and a balance, and at least the bearing of the balance includes the timepiece bearing described above. It is characterized by being used.

  With this configuration, since the magnetic attractive force of the permanent magnet acts in a state where no impact is applied to the watch bearing, the pressurization (P0 described above) can be set large. Therefore, it is possible to prevent the bearing body from moving with a slight external force applied. In addition, by accommodating the movement amount of the bearing body so as to be movable by a predetermined amount with respect to the frame body, the movement amount of the bearing body can be regulated before an external force that damages the relief portion is applied. Therefore, it is possible to provide a movement capable of improving the timing accuracy.

  In addition, a portable timepiece according to the present invention includes the above-described movement and a casing that encloses the movement.

  With this configuration, since the magnetic attractive force of the permanent magnet acts in a state where no impact is applied to the watch bearing, the pressurization (P0 described above) can be set large. Therefore, it is possible to prevent the bearing body from moving with a slight external force applied. In addition, by accommodating the movement amount of the bearing body so as to be movable by a predetermined amount with respect to the frame body, the movement amount of the bearing body can be regulated before an external force that damages the relief portion is applied. Therefore, it is possible to provide a portable timepiece that can improve the timing accuracy.

  According to the timepiece bearing according to the present invention, since the magnetic attraction force of the permanent magnet acts when no impact is applied to the timepiece bearing, the pressurization (P0 described above) can be set large. Therefore, it is possible to prevent the bearing body from moving with a slight external force applied. In addition, by accommodating the movement amount of the bearing body so as to be movable by a predetermined amount with respect to the frame body, the movement amount of the bearing body can be regulated before an external force that damages the relief portion is applied. Therefore, the timing accuracy can be improved.

FIG. 4 is a plan view of the movement front side of the mechanical timepiece according to the embodiment of the present invention (some parts are omitted and the receiving member is indicated by an imaginary line). It is a schematic fragmentary sectional view which shows the part of the escape wheel from the barrel in the embodiment of the present invention. It is a general | schematic fragmentary sectional view which shows the part of the balance from the escape wheel in embodiment of this invention. It is the A section enlarged view of FIG. 3 (1st aspect of a bearing). It is a perspective view which shows the balance and bearing in embodiment of this invention. It is a disassembled perspective view which shows the bearing of FIG. It is a graph which shows the relationship between the displacement amount of the shaft body of the bearing of the 1st aspect in embodiment of this invention, and reaction force (magnetic attraction force). It is a top view which shows the 2nd aspect of the bearing in embodiment of this invention. It is sectional drawing which follows the BB line of FIG. It is sectional drawing (equivalent to the A section of FIG. 3) which shows the 3rd aspect of the bearing unit in embodiment of this invention. It is a graph which shows the relationship between the displacement amount and reaction force (composite value) of the shaft body of the bearing of the 3rd aspect in embodiment of this invention. It is sectional drawing which shows another aspect of the arrangement | positioning method of the permanent magnet in embodiment to this invention. It is sectional drawing which shows another aspect of the arrangement | positioning method of the permanent magnet in embodiment to this invention. It is sectional drawing of the conventional earthquake-resistant bearing. It is sectional drawing of the conventional combination bearing. It is a top view which shows the structure of the conventional bearing. It is sectional drawing which follows the EE line | wire of FIG. It is a graph which shows the relationship between the displacement amount of the rotating shaft of the conventional bearing, and a spring reaction force.

  Next, an embodiment of a timepiece bearing according to the present invention will be described with reference to FIGS. In the present embodiment, the case where the timepiece bearing unit is used in a portable mechanical timepiece such as a wristwatch will be described.

(Mechanical watch)
As shown in FIGS. 1 to 3, the movement 100 of the mechanical timepiece has a base plate 102 that constitutes a substrate of the movement 100. A winding stem 110 is rotatably incorporated in the winding stem guide hole 102 a of the main plate 102. The dial 104 (see FIG. 2) is attached to the movement 100. In general, of both sides of the main plate 102, the side on which the dial plate 104 is disposed is referred to as the back side of the movement 100, and the opposite side of the side on which the dial plate 104 is disposed is referred to as the front side of the movement 100. A train wheel incorporated on the front side of the movement 100 is referred to as a front train wheel, and a train wheel incorporated on the back side of the movement 100 is referred to as a back train wheel. In addition, it is comprised as a portable timepiece by providing the movement 100 with a casing (not shown).

  The position of the winding stem 110 in the axial direction is determined by a switching device including the setting lever 190, the yoke 192, the yoke spring 194, and the back presser 196. The chisel wheel 112 is rotatably provided on the guide shaft portion of the winding stem 110. When the winding stem 110 is rotated in a state where the winding stem 110 is in the first winding stem position (0th stage) closest to the inside of the movement 100 along the rotation axis direction, the rotation of the handwheel is caused. The chic wheel 112 is rotated through. The round hole wheel 114 is rotated by the rotation of the chichi wheel 112. Further, the square hole wheel 116 is rotated by the rotation of the round hole wheel 114. As the square hole wheel 116 rotates, the mainspring 122 (see FIG. 2) accommodated in the barrel complete 120 is wound up.

  The center wheel & pinion 124 is rotated by the rotation of the barrel complete 120. The escape wheel & pinion 130 rotates through the rotation of the fourth wheel 128, the third wheel 126, and the second wheel 124. The barrel wheel 120, the second wheel 124, the third wheel 126, and the fourth wheel 128 constitute a front train wheel.

  The escapement and speed control device for controlling the rotation of the front train wheel includes a balance 140, a escape wheel 130, and an ankle 142. Based on the rotation of the center wheel & pinion 124, the cylindrical pinion 150 (see FIG. 2) rotates simultaneously. The minute hand 152 attached to the cylindrical pinion 150 displays “minute”. The cylindrical pinion 150 is provided with a slip mechanism for the center wheel & pinion 124. Based on the rotation of the hour pinion 150, the hour wheel 154 rotates through the rotation of the minute wheel. An hour hand 156 attached to the hour wheel 154 displays “hour”.

  The barrel complete 120 includes a barrel complete gear 120d, a barrel complete 120f, and a mainspring 122. The barrel complete 120f includes an upper shaft portion 120a and a lower shaft portion 120b. The barrel complete 120f is made of a metal such as carbon steel. The barrel gear 120d is formed of a metal such as brass.

  The center wheel & pinion 124 includes an upper shaft portion 124a, a lower shaft portion 124b, a pinion portion 124c, a gear portion 124d, and an abacus ball portion 124h. The pinion portion 124c of the center wheel & pinion 124 is configured to mesh with the barrel gear 120d. The upper shaft portion 124a, the lower shaft portion 124b and the abacus ball portion 124h are formed of a metal such as carbon steel. The gear portion 124d is formed of a metal such as nickel.

  The third wheel & pinion 126 includes an upper shaft portion 126a, a lower shaft portion 126b, a pinion portion 126c, and a gear portion 126d. The pinion 126c of the third wheel & pinion 126 is configured to mesh with the gear portion 124d.

  The fourth wheel & pinion 128 includes an upper shaft portion 128a, a lower shaft portion 128b, a pinion portion 128c, and a gear portion 128d. The pinion portion 128c of the fourth wheel & pinion 128 is configured to mesh with the gear portion 126d. The upper shaft portion 128a and the lower shaft portion 128b are formed of a metal such as carbon steel. The gear portion 128d is formed of a metal such as nickel.

  The escape wheel & pinion 130 includes an upper shaft portion 130a, a lower shaft portion 130b, a pinion portion 130c, and a gear portion 130d. The pinion 130c of the escape wheel & pinion 130 is configured to mesh with the gear portion 128d. The ankle 142 includes an ankle body 142d and an ankle true 142f. The ankle true 142f includes an upper shaft portion 142a and a lower shaft portion 142b.

  The barrel complete 120 is rotatably supported with respect to the main plate 102 and the barrel holder 160. That is, the upper shaft portion 120 a of the barrel complete 120 f is supported so as to be rotatable with respect to the barrel holder 160. The lower shaft part 120b of the barrel complete 120f is supported to be rotatable with respect to the main plate 102. The second wheel 124, the third wheel 126, the fourth wheel 128, and the escape wheel 130 are supported rotatably with respect to the main plate 102 and the train wheel bridge 162. That is, the upper shaft portion 124a of the center wheel & pinion 124, the upper shaft portion 126a of the third wheel & pinion 126, the upper shaft portion 128a of the fourth wheel & pinion 128, and the upper shaft portion 130a of the escape wheel & pinion 130 are And is rotatably supported. In addition, the lower shaft portion 124b of the center wheel 124, the lower shaft portion 126b of the third wheel 126, the lower shaft portion 128b of the fourth wheel 128, and the lower shaft portion 130b of the escape wheel 130 are defined with respect to the main plate 102. It is rotatably supported.

  The ankle 142 is rotatably supported with respect to the main plate 102 and the ankle receiver 164. That is, the upper shaft portion 142 a of the ankle 142 is supported so as to be rotatable with respect to the ankle receiver 164. The lower shaft portion 142b of the ankle 142 is rotatably supported with respect to the main plate 102.

  The bearing portion of the barrel holder 160 that rotatably supports the upper shaft portion 120a of the barrel complete 120f, the bearing portion of the train wheel ring 162 that rotatably supports the upper shaft portion 124a of the center wheel & pinion 124, and the third wheel & pinion 126 The bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 126a, the bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 128a of the fourth wheel & pinion 128, and the escape wheel 130 Lubricating oil is injected into the bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 130a and the bearing portion of the ankle receiver 164 that rotatably supports the upper shaft portion 142a of the ankle 142. Further, the bearing portion of the main plate 102 that rotatably supports the lower shaft portion 120b of the barrel complete 120f, the bearing portion of the main plate 102 that rotatably supports the lower shaft portion 124b of the center wheel & pinion 124, and the third wheel 126 A bearing portion of the main plate 102 that rotatably supports the lower shaft portion 126b, a bearing portion of the main plate 102 that rotatably supports the lower shaft portion 128b of the fourth wheel & pinion 128, and a lower shaft portion 130b of the escape wheel 130. Lubricating oil is injected into the bearing portion of the base plate 102 that is rotatably supported and the bearing portion of the base plate 102 that rotatably supports the lower shaft portion 142 b of the ankle 142. This lubricating oil is preferably a precision machine oil, particularly preferably a so-called watch oil.

  In order to improve the retention performance of the lubricating oil, the conical, cylindrical, or frustoconical oil sump is provided on each bearing portion of the main plate 102, the bearing portion of the barrel holder 160, and each bearing portion of the train wheel bridge 162. It is preferable to provide a part. Providing the oil reservoir can effectively prevent the oil from diffusing due to the surface tension of the lubricating oil. The main plate 102, the barrel holder 160, the train wheel bridge 162, and the ankle receiver 164 may be formed of metal such as brass, or may be formed of resin such as polycarbonate.

(Structure of balance)
Next, the structure of the balance of this embodiment will be described.
As shown in FIG. 3, the balance 140 includes a balance stem 140 a and a hairspring 140 c.

  The hairspring 140c is a thin leaf spring having a spiral shape having a plurality of winding numbers. An inner end portion of the hairspring 140c is fixed to a whistle ball 140d fixed to a balance stem (shaft body portion) 140a, and an outer end portion of the hairspring 140c is attached to a balance holder 167 so as to be rotatable. It is fixed by screwing through a beard 170a attached to 170. The outer periphery of the frame 166 containing the bearing body 181 is fixed to the balance receiver 167. The slow / fast needle 168 is rotatably attached to the balance receiver 167. Further, the balance 140 is supported so as to be rotatable with respect to the main plate 102 and the balance receiver 167.

  Here, the balance 140 is configured to be rotatable about a shaft body 143 arranged along the central axis C. The shaft body 143 includes a balance stem 140a configured as a shaft main body portion, and tenon portions 144 and 145 formed with a diameter smaller than that of the balance stem 140a at both axial ends of the balance stem 140a. In FIG. 3, the lower side portion 144 is supported to be rotatable with respect to the main plate 102, and the upper side portion 145 is supported to be rotatable with respect to the bearing body 181. The shaft body 143, the bearing body 181 and the frame body 166 constitute a bearing 180.

Then, the 1st aspect about a bearing is demonstrated.
As shown in FIG. 4, the bearing 180 is provided on the side portion 145, which is one end portion of the shaft body 143 that rotates about the central axis C, and the thrust direction (axial direction) and the radial direction of the shaft body 143 are provided. A bearing body 181 that restricts the movement in the (radial direction) and a frame body 166 formed of a magnetic body that encloses the bearing body 181 are provided.

  The tenon portion 145 is formed so as to protrude outward in the axial direction at one end portion of the shaft body 143, and the first tenon portion 146 having a diameter smaller than that of the balance stem 140 a and the axial direction of the first tense portion 146. And a second tenon portion 148 that is formed so as to protrude further outward in the axial direction from the outer end portion with a diameter smaller than that of the first tenon portion 146. That is, a stepped portion 149 is formed between the balance stem 140a and the first tenon portion 146.

  The bearing body 181 includes a hole 171 formed with a through hole 172 through which the second horn portion 148 is inserted, and a stone 173 disposed opposite to the axial end surface 148a of the second horn portion 148. .

  The hole stone 171 is made of a transparent material such as ruby, for example, and is a member having a substantially circular outer shape in which a through hole 172 is formed in the approximate center in a plan view. The inner diameter of the through-hole 172 is formed to a size that allows the second side portion 148 of the shaft body 143 to be inserted. Further, the hole stone 171 is formed in such a size that the outer peripheral surface 171 a is press-fitted and fixed to the inner peripheral surface 174 a of the hole stone frame 174.

  The stone 173 is a member having a substantially circular shape in a plan view formed of, for example, ruby. The stone 173 is arranged on the outer side in the axial direction of the hole stone 171, and is configured such that the axial end surface 148 a of the second side portion 148 of the shaft body 143 is opposed to the center of the bottom surface 173 a in plan view. ing. Further, the stone 173 is configured such that the peripheral edge 173b is placed in a notch recess 174b formed in the hole stone frame 174. In other words, the stone 173 is restricted so that it cannot move to the hole stone 171 side (inward in the axial direction) from the position where the notch recess 174b is formed. In addition, the upper surface 173c of the stone 173 is curvedly formed in a side view.

  The locking spring 182 is configured by a plate spring member made of, for example, metal. The locking spring 182 is supported and fixed on the outer side in the axial direction of the stone 173 in the hole stone frame 174. The locking spring 182 has a biasing force that restricts the stone 173 (bearing body 181) from moving outward in the axial direction. In a state where no impact is applied to the bearing 180, the locking spring 182 and the upper surface 173c of the stone 173 are in contact with each other, and the peripheral edge 173b of the stone 173 is placed in the notch recess 174b.

  The hole stone frame 174 is formed of, for example, a magnetic material such as iron or nickel alloy, and is formed in a substantially cylindrical shape with a through hole 177 formed in the axial direction. The hole stone 171, the stone 173, and the locking A spring 182 is included. Further, a taper portion 174c that is reduced in diameter toward the inner side in the axial direction is formed along the circumferential direction on the inner side in the axial direction (the side on which the shaft body 143 is disposed) in the perforated stone frame body 174. A through-hole 174e through which the relief portion 145 is inserted is formed in the bottom surface 174d of the frame body 174. Further, a groove portion 174f is formed on the inner peripheral surface 174a of the hole stone frame body 174 over the entire circumference along the circumferential direction to which the peripheral edge portion of the locking spring 182 is fitted and supported.

  Here, the configuration of the locking spring 182 and the configuration of supporting and fixing the locking spring 182 to the hole stone frame body 174 will be described using an example. For example, as shown in FIG. 5 and FIG. 6, a plurality of locking springs 182 are formed radially from the inner ring portion 182a substantially abutting on the upper surface 173c of the stone 173 and radially outward from the inner ring portion 182a. Spring portion 182b. In FIGS. 5 and 6, three spring portions 182 b are formed at approximately equal intervals in the circumferential direction. Further, a plurality of notches 174h that can be inserted through the tip of the spring portion 182b of the locking spring 182 are formed on one surface 174g of the hole stone frame 174 in accordance with the shape of the spring portion 182b. Furthermore, a groove portion 174f is formed on the inner peripheral surface 174a of the hole stone frame 174 over the entire circumference along the circumferential direction to which the tip of the spring portion 182b is fitted and supported. And the notch part 174h and the groove part 174f are connected. That is, by inserting the tip of the spring part 182b in accordance with the position of the notch part 174h, the tip of the spring part 182b can be arranged in the groove part 174f, and in this state, the locking spring 182 is placed in the hole stone frame 174. In contrast, the spring portion 182b of the locking spring 182 can be supported and fixed to the perforated stone frame 174 by rotating in the circumferential direction and supporting and fixing the tip of the spring portion 182b to the groove portion 174f.

  Returning to FIG. 4, the frame body 166 is formed of, for example, a magnetic body such as iron or nickel alloy, and is formed in a substantially cylindrical shape having a through hole 188 formed in the axial direction. The frame body 166 includes the bearing body 181. Yes. In addition, a taper portion 166c having a diameter reduced toward the inner side in the axial direction is formed on the inner side in the axial direction of the frame body 166 (the side on which the shaft body 143 is disposed). A through hole 166e through which the portion 145 is inserted is formed. Further, the radial length of the through hole 188 is set so that a gap is formed between the inner peripheral surface 166a of the frame body 166 and the outer peripheral surface 174i of the perforated stone frame body 174. That is, the hole stone frame 174 is configured to move in the radial direction and the thrust direction with respect to the frame 166.

  A gap d <b> 1 is formed between the bottom surface 166 d of the frame body 166 and the stepped portion 149 of the shaft body 143 in a state where no external impact is applied to the bearing 180. By forming the gap d1, the shaft body 143 can move outward in the axial direction by the gap d1 when an external impact is applied to the bearing 180.

  Here, as shown in FIG. 4, a recessed portion 166k is formed along the circumferential direction at a position facing the hole stone frame 174 in the tapered portion 166c of the frame 166, and a permanent magnet is formed in the recessed portion 166k. 176 is provided. The permanent magnet 176 is arranged so that the north pole is located on the outer side in the axial direction and the south pole is located on the inner side in the axial direction, and is supported and fixed in the recessed portion 166k. That is, the N pole of the permanent magnet 176 is arranged so as to face the hole stone frame 174.

  The bearing 180 configured as described above rotates about the central axis C while the shaft body 143 (the side portion 145) is supported by the bearing body 181. Here, since the permanent magnet 176 is arranged on the frame body 166, a flow of magnetic flux (arrow B in FIG. 4) is generated between the permanent magnet 176 and the hole stone frame body 174. By arranging the permanent magnets 176 substantially evenly along the circumferential direction of the shaft body 143 (the tenon portion 145), the shaft center of the tenon portion 145 and the shaft center of the hole stone 171 can be substantially matched.

  Further, as shown in FIG. 7, by arranging the permanent magnet 176, the permanent magnet 176 and the hole stone frame can be obtained in a state where the hole stone frame body 174 is not displaced (a state where no external force is applied to the bearing 180). A magnetic attractive force P0 ′ is acting between the body 174 and the body 174. When the position of the shaft body 143 is displaced by applying an external force to the bearing 180 from this state, the perforated frame body 174 (bearing body 181) moves in the radial direction and the thrust direction with respect to the frame body 166. Then, the attractive force acting between the permanent magnet 176 and the hole stone frame 174 is reduced. When the displacement amount of the shaft body 143 increases, the stepped portion 149 of the shaft body 143 comes into contact with the bottom surface 166d of the frame body 166, so that the movement of the shaft body 143 in the thrust direction is restricted. Displacement is also restricted. When the magnetic attraction force when the step 149 of the shaft body 143 contacts the bottom surface 166d of the frame body 166 is P1 ′, P1 ′ is inevitably smaller than the tenon breakage strength P2. Further, since the bearing 180 has characteristics as shown in FIG. 7, P0 ′ can be set to a value smaller than the tenon breakage strength P2 and larger than the conventional P0. In addition, when the external force applied to the bearing 180 is lost, it returns to the original position smoothly by the magnetic attractive force of the taper portion formed in the frame body 166 and the hole stone frame body 174 and the permanent magnet 176.

  According to the present embodiment, the magnetic attractive force P0 ′ of the permanent magnet 176 acts when no external force is applied to the bearing 180, and the attractive force is applied as the shaft body 143 (hole stone frame 174) moves due to the applied external force. Gradually becomes smaller. Therefore, the magnetic attractive force P0 ′ that is the initial value can be set larger than the conventional value. As a result, it is possible to prevent the hole stone frame body 174 (bearing body 181) from moving with only a slight external force applied. Further, a stepped portion 149 is formed on the shaft body 143, and the stepped portion 149 abuts against the bottom surface 166d of the frame body 166, thereby restricting the movement of the shaft body 143 in the axial direction. The amount of movement of the bearing body 181 can be regulated before the damaging external force P2 is applied. Therefore, the timing accuracy can be improved.

Then, the 2nd aspect (bearing 280) of the bearing demonstrated by the said embodiment is demonstrated. In addition, about a 2nd aspect, since only the structure of a hole stone frame and a frame differs from a 1st aspect, the location from which a structure differs is mainly demonstrated.
As shown in FIGS. 8 and 9, the hole frame 274 is formed of a magnetic material such as iron or nickel alloy, and is formed in a substantially cylindrical shape in which a through hole 277 is formed in the axial direction. A hole stone 171, a stone 173 and a locking spring 182 are included. Further, a taper portion 274c that is reduced in diameter toward the inner side in the axial direction is formed on the inner side in the axial direction (the side on which the shaft body 143 is disposed) of the perforated stone frame body 274. A through-hole 274e through which the relief portion 145 is inserted is formed in 274d. Furthermore, a groove portion 274f is formed on the inner peripheral surface 274a of the hole stone frame body 274 over the entire circumference along which the peripheral edge portion of the locking spring 182 is fitted and supported. A locking projection 274j is formed on the outer peripheral surface 274i of the hole stone frame 274 so as to protrude outward in the radial direction. 8 and 9, the locking protrusions 274j are formed at three locations at substantially equal intervals in the circumferential direction.

  The frame body 266 is formed of, for example, a magnetic material such as iron or nickel alloy, is formed in a substantially cylindrical shape having a through hole 288 formed in the axial direction, and includes the bearing body 181. Further, a taper portion 266c having a diameter reduced toward the inner side in the axial direction is formed on the inner side in the axial direction of the frame body 266 (the side on which the shaft body 143 is disposed). A through hole 266e through which the portion 145 is inserted is formed. Further, the radial length of the through hole 288 is set so that a gap is formed between the inner peripheral surface 266a of the frame body 266 and the outer peripheral surface 274i of the perforated frame body 274. That is, the hole stone frame 274 is configured to be movable in the radial direction and the thrust direction with respect to the frame 266.

  In addition, a plurality of notches 266h through which the tips of the locking projections 274j of the hole stone frame 274 can be inserted are formed on one surface 266g of the frame 266 in accordance with the shape of the locking projections 274j. Furthermore, a groove portion 266f is formed on the inner peripheral surface 266a of the frame body 266 along the circumferential direction so as to support the tip of the locking projection 274j over the entire circumference. And the notch part 266h and the groove part 266f are connected. That is, by inserting the front end of the locking projection 274j in accordance with the position of the notch portion 266h, the front end of the locking projection 274j can be disposed in the groove portion 266f, and in this state, the cobblestone frame 274 is attached to the frame body 266. The locking protrusion 274j of the perforated frame body 274 can be supported by the frame body 266 by rotating in the circumferential direction relative to the groove portion 266f. . The groove 266f is formed to be slightly larger in the radial direction and the thrust direction than the locking protrusion 274j. In other words, the hole stone frame body 274 is allowed to move in the radial direction and the thrust direction with respect to the frame body 266, and the hole stone frame body 274 is configured not to move more than a predetermined amount with respect to the frame body 266. Has been.

  Here, as shown in FIG. 9, a recessed portion 266k is formed along the circumferential direction at a position facing the hole stone frame 274 in the tapered portion 266c of the frame 266, and the recessed portion 266k has a permanent magnet. 176 is provided. The permanent magnet 176 is arranged so that the N pole is located on the outer side in the axial direction and the S pole is located on the inner side in the axial direction, and is supported and fixed in the recessed portion 266k. That is, the N pole of the permanent magnet 176 is arranged so as to face the perforated stone frame body 274.

  The bearing 280 configured as described above rotates around the central axis C while the shaft body 143 (the side portion 145) is supported by the bearing body 181. Here, since the permanent magnet 176 is arranged on the frame body 266, a flow of magnetic flux (arrow B in FIG. 4) is generated between the permanent magnet 176 and the hole stone frame body 274. By arranging the permanent magnets 176 substantially evenly along the circumferential direction of the shaft body 143 (the tenon portion 145), the shaft center of the tenon portion 145 and the shaft center of the hole stone 171 can be substantially matched.

  Further, as shown in FIG. 7, by arranging the permanent magnet 176, the permanent magnet 176 and the hole stone frame can be obtained in a state where the hole stone frame body 274 is not displaced (a state where no external force is applied to the bearing 280). A magnetic attractive force P0 ′ is acting between the body 274 and the body 274. When the position of the shaft body 143 is displaced by applying an external force to the bearing 280 from this state, the perforated frame body 274 (bearing body 181) moves in the radial direction and the thrust direction with respect to the frame body 266. Then, the attractive force acting between the permanent magnet 176 and the hole stone frame 274 is reduced. When the displacement amount of the shaft body 143 increases, the stepped portion 149 of the shaft body 143 comes into contact with the bottom surface 266d of the frame body 266, thereby restricting the movement of the shaft body 143 in the thrust direction. Further, the locking projection 274j of the hole stone frame 174 abuts against the radially outer end surface and the axial outer end surface of the groove 266f of the frame body 266, so that the displacement of the hole stone frame 274 with respect to the frame body 266 is also restricted. . When the magnetic attraction force when the stepped portion 149 of the shaft body 143 contacts the bottom surface 266d of the frame body 266 is P1 ′, P1 ′ is inevitably smaller than the tenon breakage strength P2. Further, since the bearing 280 has characteristics as shown in FIG. 7, P0 ′ can be set to a value smaller than the tenon breakage strength P2 and larger than the conventional P0.

Subsequently, the third aspect (bearing 380) of the bearing described in the above embodiment will be described. In addition, about a 3rd aspect, since only the structure of a frame differs from a 1st aspect, the location from which a structure differs is mainly demonstrated.
As shown in FIG. 10, the frame 366 is formed of a magnetic material such as iron or nickel alloy, for example, is formed in a substantially cylindrical shape with a through hole 388 formed in the axial direction, and includes the bearing body 181. is doing. Further, a tapered portion 366c having a diameter reduced toward the inner side in the axial direction is formed on the inner side in the axial direction of the frame 366 (the side on which the shaft 143 is disposed). A through hole 366e through which the portion 145 is inserted is formed. Further, the radial length of the through hole 388 is set so that a gap is formed between the inner peripheral surface 366a of the frame body 366 and the outer peripheral surface 174i of the perforated stone frame body 174. That is, the hole stone frame 174 is configured to move in the radial direction and the thrust direction with respect to the frame 366. Further, a presser spring 382 having a biasing force against the bearing body 181 is provided on the axially outer side in the through hole 388 of the inner frame 366. The configuration of the presser spring 382 and the configuration of supporting and fixing the presser spring 382 to the frame body 366 are substantially the same as the configuration of the locking spring 182 and the configuration of supporting and fixing the locking spring 182 to the hole stone frame 174 described above. It is.

  Here, a recessed portion 366k is formed along the circumferential direction at a position facing the hole stone frame 174 in the tapered portion 366c of the frame 366, and a permanent magnet 176 is provided in the recessed portion 366k. The permanent magnet 176 is arranged so that the north pole is located on the outer side in the axial direction and the south pole is located on the inner side in the axial direction, and is supported and fixed in the recessed portion 366k. That is, the N pole of the permanent magnet 176 is arranged so as to face the hole stone frame 174.

  The bearing 380 configured as described above rotates about the central axis C while the shaft body 143 (the side portion 145) is supported by the bearing body 181. Here, since the permanent magnet 176 is disposed on the frame body 366, a flow of magnetic flux (arrow B in FIG. 4) is generated between the permanent magnet 176 and the hole stone frame body 174. By arranging the permanent magnets 176 substantially evenly along the circumferential direction of the shaft body 143 (the tenon portion 145), the shaft center of the tenon portion 145 and the shaft center of the hole stone 171 can be substantially matched.

  In addition, as shown in FIG. 11, by providing the permanent magnet 176, the permanent magnet 176 and the hole stone frame can be obtained in a state where the hole stone frame body 174 is not displaced (a state where no external force is applied to the bearing 380). A magnetic attractive force P0 ′ is acting between the body 174 and the body 174. Further, a spring reaction force P 0 of the presser spring 382 is applied to the hole stone frame 174. That is, a force of P0 ″ (= P0 + P0 ′) is working. When the position of the shaft body 143 is displaced by applying an external force to the bearing 380 from this state, the hole stone frame body 174 (bearing body 181) is moved. It moves in the radial direction and the thrust direction with respect to the frame body 366. Then, the attractive force acting between the permanent magnet 176 and the hole stone frame body 174 decreases, and the pressing spring 382 causes the hole stone frame body 174 to move. 11, the force applied when the shaft body 143 is displaced is the total value of the magnetic attractive force and the spring reaction force, and the maximum value and the minimum value. As a result, the step 149 of the shaft body 143 comes into contact with the bottom surface 366d of the frame body 366 to increase the displacement of the shaft body 143. Sura Movement in the G direction is also restricted, and the displacement of the hole frame 174 is also restricted. When the magnetic attraction force when the step 149 of the shaft 143 contacts the bottom surface 166d of the frame 166 is P1 ″, P1 "" Can be easily set smaller than the tenon breakage strength P2. That is, since the bearing 380 has the characteristics shown in FIG. 11, P0 "is smaller than the tenon breakage strength P2 and is smaller than the conventional P0. A large value can be set.

  Note that the present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention. That is, the specific shapes, configurations, and the like given in the embodiment are merely examples, and can be changed as appropriate.

  For example, in the above embodiment, the case where the bearing 180 is provided on the side portion 145 has been described. However, the bearing 180 may be disposed on the side portion 144 side.

  Moreover, in the said embodiment, although the permanent magnet 176 demonstrated the case where it arrange | positions so that an N pole may be located in an axial direction outer side and an S pole may be located in an axial direction inner side, for example, as shown in FIG. The recessed portion 166k may be formed so as to be parallel to the inclined surface of the tapered portion 166c, and the permanent magnet 176 may be disposed so as to face the tapered portion 174c of the hole stone frame 174.

  Moreover, in the said embodiment, although the permanent magnet 176 demonstrated the case where it arrange | positions so that a north pole may be located in an axial direction outer side, and a south pole may be located inside an axial direction, for example, as shown in FIG. The permanent magnet 176 may be arranged so that the north pole and the south pole are positioned radially outward. Further, the positions of the N pole and S pole of the permanent magnet may be reversed.

  Furthermore, in the above embodiment, the case where the locking projection 274j is formed in the hole stone frame body 274 and the groove portion 266f is formed in the frame body 266 has been described. However, the locking protrusion is formed in the frame body and the hole stone frame is formed. Grooves may be formed in the body.

  In the embodiment described above, the case where the bearing 180 having the above-described configuration is adopted as the bearing to be disposed on the balance 140 has been described. However, in addition to the balance 140, the barrel wheel 120, the second wheel 124, the third wheel 126, and the fourth wheel. The bearing 180 having the above-described configuration may be employed as the bearing of the number wheel 128, escape wheel 130 and ankle 142.

  DESCRIPTION OF SYMBOLS 100 ... Movement 120 ... Incense box car (incense box) 124 ... Second car (car wheel) 126 ... Third car (car wheel) 128 ... Fourth car (car wheel) 130 ... Spar wheel 140 ... Temp 140a ... Tenshin (Shaft body part) 142 ... ankle 143 ... shaft body 145 ... horn part 148a ... end face (axial direction end face) 166 ... frame body 166e ... through hole 171 ... hole stone 172 ... through hole 173 ... stone 174 ... hole stone frame body 176 ... Permanent magnet 180 ... Bearing (clock bearing) 181 ... Bearing body 182 ... Locking spring 266 ... Frame body 266f ... Groove (locking recess) 274 ... Hole stone frame 274j ... Locking projection 366 ... Frame body 382 ... Presser spring (elastic member) C ... Center axis (axis center)

Claims (7)

A shaft that rotates about its axis;
A timepiece bearing comprising: a bearing body provided at at least one axial end of the shaft body and rotatably supporting the shaft body,
The shaft body is
The shaft body,
A tenon portion formed at the axial end of the shaft body portion,
The bearing body is
A hole stone formed with a through hole through which the ridge portion is inserted;
A receiving stone disposed opposite to the axial end surface of the ridge part;
A locking spring for restricting movement of the stone in the axial direction;
A hole stone frame body that contains the hole stone, the stone, and the locking spring;
The bearing body is accommodated so as to be movable in a predetermined amount in the axial direction and the radial direction with respect to the frame body,
At least one of the hole stone frame and the frame is formed of a magnetic material, and a permanent magnet is provided along the circumferential direction of the shaft body at a position facing the one side of the other. A watch bearing characterized by that.   2. The timepiece bearing according to claim 1, wherein both the hole stone frame and the frame are formed of a magnetic material. The shaft main body portion has a diameter larger than that of the tenon portion,
The hole diameter of the through-hole through which the tenon portion formed in the frame body can be inserted is smaller than the outer shape of the shaft main body portion,
2. The timepiece bearing according to claim 1, wherein an amount of movement of the bearing body in the axial direction is restricted by the shaft main body portion coming into contact with the frame body. A locking projection is formed on one of the frame and the hole stone frame, and a locking recess is formed on the other to lock the locking projection,
The timepiece bearing according to claim 1, wherein an axial movement amount of the bearing body is restricted with respect to the frame body. An elastic member for elastically holding the movement of the bearing body in the axial direction is disposed;
The timepiece bearing according to claim 1, wherein an amount of movement of the bearing body in the axial direction is restricted with respect to the frame body. Watch movement with barrel, watch wheel, escape wheel, ankle and balance,
A timepiece bearing according to any one of claims 1 to 4 is used at least for the balance bearing. A movement according to claim 6;
A portable timepiece comprising a casing containing the movement.

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